EP1029724A2 - Kältemittelentspannungsanlage für eine Fahrzeugklimaanlage - Google Patents

Kältemittelentspannungsanlage für eine Fahrzeugklimaanlage Download PDF

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Publication number
EP1029724A2
EP1029724A2 EP00301195A EP00301195A EP1029724A2 EP 1029724 A2 EP1029724 A2 EP 1029724A2 EP 00301195 A EP00301195 A EP 00301195A EP 00301195 A EP00301195 A EP 00301195A EP 1029724 A2 EP1029724 A2 EP 1029724A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
section
relief
air conditioning
vehicle
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP00301195A
Other languages
English (en)
French (fr)
Other versions
EP1029724B1 (de
EP1029724A3 (de
Inventor
Yuichi Kato
Koji Kikuchi
Satoshi Ogihara
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nissan Motor Co Ltd
Original Assignee
Nissan Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nissan Motor Co Ltd filed Critical Nissan Motor Co Ltd
Publication of EP1029724A2 publication Critical patent/EP1029724A2/de
Publication of EP1029724A3 publication Critical patent/EP1029724A3/de
Application granted granted Critical
Publication of EP1029724B1 publication Critical patent/EP1029724B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3225—Cooling devices using compression characterised by safety arrangements, e.g. compressor anti-seizure means or by signalling devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the present invention relates to a refrigerant relief device for a vehicle air conditioner and particularly relates to a refrigerant relief device for a vehicle air conditioner provided with a so-called air conditioning cycle.
  • the pressure of a passage having the high pressure in the air conditioning cycle for example, the pressure of a passage from the discharge portion of the condenser to the expansion valve, is disadvantageously high relative to that in case of using a conventional refrigerant.
  • This tendency is by no means desirable in consideration that the area in which the air conditioning cycle functions is within a vehicle applied with various external forces and sometimes an impact depending on the travel condition or the like.
  • an object of the present invention to provide a refrigerant relief device for a vehicle air conditioner capable of surely, promptly reducing the pressure of the air conditioning cycle when required.
  • a refrigerant relief device for a vehicle air conditioner is provided with detection means for detecting an impact applied to the vehicle, relief means for relieving a refrigerant at a high pressure side of an air conditioning cycle of the vehicle air conditioner to an outside of the air conditioning cycle, and control means for controlling the relief means so as to relieve the refrigerant at the high pressure side of the air conditioning cycle to the outside of the air conditioning cycle when the detection means detects the impact.
  • reference symbol FR denotes the front side of a vehicle V
  • L denotes the left side of the vehicle V
  • R denotes the right side of the vehicle V
  • UPR denotes the upper side of the vehicle V.
  • a condenser 10 constitutes a part of the air conditioning cycle of a vehicle air conditioner S which uses carbon dioxide as a refrigerant.
  • the condenser 10 is disposed crosswise at the front portion of an engine room B.
  • the refrigerant compressed by a compressor 60 flows into the upper tank 13 of the condenser 10 from a pipe 40a and reaches a lower tank 11 thereof, while flowing in a core 14 in parallel between the right and left end portions thereof so as to radiate heat into the atmosphere, and then flows into a liquid tank 70 through a pipe 40b.
  • the pressure-reduced refrigerant absorbs the heat of the air-conditioning blow in an evaporator which is not shown and then flows to the compressor 60.
  • the lower tank 11 of the condenser 10 is provided with solenoid type relief valves 20 serving as relief means at right and left positions of the tank 11, respectively. Although a single relief valve 20 may suffice, two relief valves 20 allow pressure to be relieved outside more promptly.
  • Each of the solenoid type relief valves 20 has a coil 21 shown in Fig. 4. a movable iron core 22 inserted into the coil 21, a push rod 23 coupled to the movable iron core 22, and a fixed iron core 24 provided below the movable iron core 22. A spool 26 is coupled to the push rod 23 through a joint 25.
  • the spool 26 is inserted into a longitudinal moving space 11A formed in the lower tank 11, to be movable vertically, and sealed by two portions, i.e., the joint 25 and a lower flange portion 26a.
  • the spool 26 is urged upward by a disk spring 27 provided below the flange portion 26a.
  • Upper and lower seal portions 26b of truncated cone shape are formed at the spool 26.
  • Two reception portions 11a corresponding to the seal portions 26b are formed at the lower tank 11. As shown in FIG. 4, when the relief valve 20 is closed, the seal portions 26b are pressed against the reception portions 11a by the urging force of the disc spring 27 to thereby seal the refrigerant.
  • Upper and lower passages 11C communicating between the refrigerant chamber 11B and the moving space 11A are formed in the lower tank 11.
  • a relief passage 11D communicating between the space 11A and the outside of the valve 20 is also formed in the lower tank 11.
  • the relief passage 11D is provided to relieve the pressure of the refrigerant chamber 11B to the outside.
  • the external side opening of the relief passage 11D is formed in the vehicle rear side wall surface of the lower tank 11. Due to this, pressure relief direction is directed inward of the engine room B.
  • the coils 21 are connected to a CPU 31 through a valve driver section 30 and a G sensor (detection means) 32, which is an acceleration sensor used to control an airbag system 33, is connected to the CPU 31.
  • G sensor detection means
  • the solenoid type relief valve 20 is also controlled by using this G sensor 32.
  • the CPU 31 in response to the sensing of the G sensor 32, supplies current to the respective coils 21 of the relief valve 20 through the valve driver section 30 and excites them. Since the movable iron core 22 is attracted toward the fixed iron core 24 side by the electromagnetic force resulted from this excitation, the push rod 23 goes down and pushes down the spool 26 against the urging force of the disk spring 27 and then the sealing states of the upper and lower seal portions 26b are released (to thereby open the relief valve 22). As a result, the space 11A is communicated with the relief passage 11D.
  • a predetermined value for example, an impact due to the collision of the vehicle V or the like
  • the high pressure refrigerant within the lower tank 11 flows into the relief passage 11D through the passage 11C and the space 11A, drives the rubber plug 12 away from the space 11D, and ejects toward the inside of the engine room B.
  • the high pressure of the refrigerant chamber 11A is relieved to the outside of the valve 20 and the high pressure of the air conditioning cycle is thereby reduced promptly.
  • the impact applied to the vehicle is sensed and the pressure of the high pressure side of the air conditioning cycle is controlled to be discharged from the relief valve to the outside thereof. Due to this, in such a case, i.e., in case of the application of the impact to the vehicle, it is possible to promptly, surely reduce the pressure of the air conditioning cycle.
  • the refrigerant relief device in this embodiment is basically the same in overall construction as that in the first embodiment, it differs in the construction of the relief valve. It is noted that the same constituent elements in the refrigerant relief device in this embodiment as those in the first embodiment are denoted by the same reference symbols as those in the first embodiment and that description to their concrete constructions will not be given herein.
  • an inflater type relief valve 50 instead of the solenoid type relief valve 20 in the first embodiment 1, is used as shown in FIG. 5.
  • the inflater 51 causes an ignition agent I to be burned by an electric ignition device 51a called squib to burn a gas generating agent G, thereby generating a gas as in the case of that used in an ordinary airbag system.
  • a G sensor 32 and a CPU 31.
  • the CPU 31 outputs a drive signal and drives the electric ignition device 51a through a driver section 60.
  • a cylinder portion 52 having a piston 52a is provided below the inflater 51.
  • the gas generated by burning the gas generating agent G is filled within a cylinder upper chamber 52b through a filter 53 as indicated by arrows in FIG. 5, pressure is generated and the piston 52a is pressed downward by the generated pressure.
  • a spool 26 similar to that shown in FIG. 4 is coupled, through a joint 25, to the tip end portion of the piston 52a. As the piston 52a goes down, the spool 26 goes down, too.
  • the lower construction of the cylinder portion 52 is exactly the same as the lower construction of the valve in the first embodiment. Namely, as the spool 26 goes down, the relief valve 50 is opened and the high pressure refrigerant within a refrigerant chamber 11B of a lower tank 11 is relieved to the outside of the valve 50.
  • an impact applied to the vehicle is sensed and the pressure of the high pressure side of the air conditioning cycle is controlled to be discharged from the relief valve to the outside thereof.
  • the pressure of the high pressure side of the air conditioning cycle is controlled to be discharged from the relief valve to the outside thereof.
  • the advantage of providing the relief valve at the condenser having the highest pressure in the air conditioning cycle and that of providing the relief valve at the rear side of the condenser and directing the discharge direction of the refrigerant toward the inside of the engine room in this embodiment are the same as those in the first embodiment.
  • discharge direction of the refrigerant gas is directed toward the inside of the engine room in the above-stated embodiments, the direction should not be limited thereto. It may be set to be directed downward of the engine room. Any other direction which has less influence applied to the outside of the valve can be appropriately set.
  • the position at which the relief valve is installed should not be limited to the condenser itself. Any other position which is on the passage at the high pressure side of the air conditioning cycle can be appropriately set in view of the vehicle layout or the like.
  • the G sensor is used to sense the impact on the vehicle and the relief valve is electrically actuated under the control of the CPU. It is also possible to actuate the relief valve by a simpler mechanical construction and directly using the impact applied on the vehicle.
  • a construction in which a valve member for opening the seal portions is provided at the condenser and a connecting member such as a link member mechanically connecting between a vehicle front side portion such as a front bumper and the valve member is also provided, is applicable.
  • the connecting member when an impact load is applied to the vehicle front side portion, the connecting member functions as, for example, a type of a sensor and a controller. Namely, when the vehicle front side is deformed, the connecting member goes backward and directly opens the valve member, thereby relieving the pressure within the air conditioning cycle.
  • the refrigerant should not be limited thereto and other refrigerants used as high pressure refrigerants in the air conditioning cycle may be applicable.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Air Bags (AREA)
EP00301195A 1999-02-16 2000-02-16 Kältemittelentspannungsanlage für eine Fahrzeugklimaanlage Expired - Lifetime EP1029724B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP3751499 1999-02-16
JP11037514A JP2000233638A (ja) 1999-02-16 1999-02-16 車両用空調装置の安全装置

Publications (3)

Publication Number Publication Date
EP1029724A2 true EP1029724A2 (de) 2000-08-23
EP1029724A3 EP1029724A3 (de) 2002-03-13
EP1029724B1 EP1029724B1 (de) 2004-02-04

Family

ID=12499658

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00301195A Expired - Lifetime EP1029724B1 (de) 1999-02-16 2000-02-16 Kältemittelentspannungsanlage für eine Fahrzeugklimaanlage

Country Status (4)

Country Link
US (1) US6240738B1 (de)
EP (1) EP1029724B1 (de)
JP (1) JP2000233638A (de)
DE (1) DE60008028T2 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1481827A1 (de) * 2003-05-27 2004-12-01 Sanden Corporation Klimatisierungssystem für ein Fahrzeug
EP1584506A1 (de) * 2004-04-06 2005-10-12 Tgk Company, Ltd. Klimaanlage mit einer Vorrichtung zum Ablassen des Kältemittels aus dem Kältekreislauf
WO2007087992A1 (de) * 2006-02-02 2007-08-09 Thomas Magnete Gmbh Expansionsventil für eine klimaanlage
US7730735B2 (en) 2007-05-22 2010-06-08 Maruya Richard H Refrigerant service port valve for air conditioners
DE102015108122A1 (de) * 2015-05-22 2016-11-24 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Kraftfahrzeug

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10161254A1 (de) * 2001-12-13 2003-07-03 Konvekta Ag Klimatisierungseinrichtung für ein Fahrzeug
DE10345835B4 (de) * 2003-10-02 2015-04-09 Bayerische Motoren Werke Aktiengesellschaft Sensoranordnung zur Überwachung von mindestens zwei physikalischen Größen
US7287399B2 (en) * 2004-02-17 2007-10-30 Obrist Engineering Gmbh Collector for the liquid phase of the working medium of an air-conditioning system
JP2005273930A (ja) * 2004-03-23 2005-10-06 Tgk Co Ltd 冷媒リリーフ装置
US7373944B2 (en) * 2004-12-27 2008-05-20 Autoliv Asp, Inc. Pyrotechnic relief valve
JP2007303747A (ja) * 2006-05-11 2007-11-22 Denso Corp 冷凍サイクルおよび冷凍サイクル用部品組立体
JP2007303746A (ja) * 2006-05-11 2007-11-22 Denso Corp 冷凍サイクルおよび冷凍サイクル用部品組立体
JP4821453B2 (ja) * 2006-06-22 2011-11-24 日産自動車株式会社 カーエアコン用電動コンプレッサのハーネス保護構造
US7677049B2 (en) * 2007-02-28 2010-03-16 Delphi Technologies, Inc. Algorithm for activation of directed relief system from vehicle accelerometers during crash
JP5075439B2 (ja) * 2007-03-26 2012-11-21 株式会社ネリキ 冷媒注入用マニホールド弁
WO2009091398A1 (en) * 2008-01-17 2009-07-23 Carrier Corporation Mounting of pressure relief devices in a high pressure refrigeration system
US8205631B2 (en) * 2008-11-19 2012-06-26 Autoliv Asp, Inc. Active material actuated vent valve
DE102009011797B4 (de) * 2009-03-05 2014-06-26 Airbus Operations Gmbh Verfahren zum Betreiben eines Kühlsystems sowie Kühlsystem
US8671967B2 (en) * 2009-08-07 2014-03-18 Autoliv Asp, Inc. Relief valve
DE102010004804A1 (de) * 2010-01-16 2011-07-21 GM Global Technology Operations LLC, ( n. d. Ges. d. Staates Delaware ), Mich. Klimaanlage eines Kraftfahrzeugs
JP6424936B1 (ja) * 2017-10-04 2018-11-21 日本電気株式会社 気液分離装置、リアドア、冷却装置、及び気液分離方法
GB2576732B (en) 2018-08-29 2020-12-30 Ford Global Tech Llc A motor vehicle assembly having improved collision integrity

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US4133186A (en) * 1977-10-17 1979-01-09 General Motors Corporation Combined electrical cut-off and relief valve
DE4207859A1 (de) * 1992-03-12 1993-09-16 Bayerische Motoren Werke Ag Kaeltemittelkreislauf einer fahrzeug-klimaanlage
DE4411281B4 (de) * 1994-03-31 2004-07-22 Daimlerchrysler Ag Kraftfahrzeug mit einer Klimaanlage
JP3339268B2 (ja) * 1995-09-12 2002-10-28 株式会社デンソー 車両用空調装置
JP3038681B2 (ja) * 1995-12-13 2000-05-08 サンデン株式会社 圧縮機の安全弁
DE19646849C1 (de) * 1996-11-13 1998-05-07 Daimler Benz Ag Klimaanlage eines Kraftfahrzeuges

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1481827A1 (de) * 2003-05-27 2004-12-01 Sanden Corporation Klimatisierungssystem für ein Fahrzeug
US7028496B2 (en) 2003-05-27 2006-04-18 Sanden Corporation Air-conditioning system for vehicle
EP1584506A1 (de) * 2004-04-06 2005-10-12 Tgk Company, Ltd. Klimaanlage mit einer Vorrichtung zum Ablassen des Kältemittels aus dem Kältekreislauf
US7165421B2 (en) 2004-04-06 2007-01-23 Tgk Co., Ltd. Refrigeration system
WO2007087992A1 (de) * 2006-02-02 2007-08-09 Thomas Magnete Gmbh Expansionsventil für eine klimaanlage
US7730735B2 (en) 2007-05-22 2010-06-08 Maruya Richard H Refrigerant service port valve for air conditioners
DE102015108122A1 (de) * 2015-05-22 2016-11-24 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Kraftfahrzeug

Also Published As

Publication number Publication date
EP1029724B1 (de) 2004-02-04
DE60008028D1 (de) 2004-03-11
EP1029724A3 (de) 2002-03-13
US6240738B1 (en) 2001-06-05
JP2000233638A (ja) 2000-08-29
DE60008028T2 (de) 2004-12-09

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